JP2022007748A - Planetary gear device - Google Patents

Abstract

To provide a planetary gear device for achieving a lower cost while actualizing high-speed rotation of a sun gear and a planetary gear.SOLUTION: On an outer periphery of a sun support shaft 31 supporting a sun gear 51, a sun supply oil passage 100 is formed to supply lubricating oil between the sun gear 51 and the sun support shaft 31. On a planetary support shaft 54 supporting the planetary gear 52, a planetary supply oil passage 102 is formed to supply lubricating oil between the planetary support shaft 54 and the planetary gear 52. A supply oil passage 103 connecting the sun supply oil passage 100 and the planetary supply oil passage 102 is extended in a direction along a radial direction of a carrier 70 and formed along the carrier 70. The supply oil passage 103 takes in the lubricating oil from the sun supply oil passage 100 with the rotation of the carrier 70, and supplies the taken-in lubricating oil to the planetary supply oil passage 102.SELECTED DRAWING: Figure 9

Description

The present invention relates to a planetary gear device.

The planetary gear device rotates, for example, a sun gear, a planetary gear that meshes with the sun gear, an internal tooth gear that meshes with the planetary gear, and the planetary gear, as in the planetary gear mechanism disclosed in Patent Document 1. A carrier that is capable of supporting and revolving around the sun gear and that rotates around the axis of the sun gear together with the planetary gear is provided.

JP-A-2019-95058

When a planetary gear device is provided in, for example, a traveling transmission device of a tractor, it rotates at a high speed to transmit power. Therefore, a planetary gear device capable of rotating a sun gear and a planetary gear at a high speed is desired.

The present invention provides a planetary gear device capable of rotating a sun gear and a planetary gear at high speed.

The planetary gear device according to the present invention is
The sun gear, the planetary gear that meshes with the sun gear, the internal tooth gear that meshes with the planetary gear, and the planetary gear that rotatably supports the planetary gear and revolves around the sun gear. A planetary gear device provided with a carrier that rotates around the axis of the sun gear as the center of rotation, which is formed on the outer peripheral portion of a sun support shaft that rotatably supports the sun gear, and is formed on the sun gear and the sun gear. A solar refueling path for supplying lubricating oil between the sun support shaft and a planetary support shaft provided on the carrier in a state of rotatably supporting the planetary gear, and the planetary support shaft and the planetary gear The planetary refueling passage for supplying lubricating oil, the solar refueling passage, and the planetary refueling passage are connected to each other, and the carrier is formed so as to extend in the radial direction and along the carrier. A supply oil passage that takes in lubricating oil from the solar refueling passage by rotation of a carrier and supplies the taken-in lubricating oil to the planetary refueling passage is provided.

According to this configuration, the lubricating oil is supplied between the sun support shaft and the sun gear by the sun refueling path, so that the sun gear can rotate smoothly. By rotating the carrier, the supply oil passage feeds the lubricating oil taken in from the solar oil passage into the planetary oil passage, and the lubricating oil supplied by the planetary oil passage is supplied to the planetary shaft and the planetary gear. Since it is supplied in between, the planetary gear can rotate smoothly, so that the sun gear and the planetary gear can be rotated at high speed. Further, since the rotation of the carrier is utilized as the power source for the lubrication supply, it is not necessary to provide a separate power source.

In the present invention
The upstream oil passage portion that opens to the solar oil supply passage, the downstream oil passage portion that opens to the planetary oil supply passage, the upstream oil passage portion, and the downstream oil passage portion are connected to the supply oil passage. A connecting oil passage portion is provided, and in the supply oil passage portion, the oil passage width in the direction along the axis direction of the sun gear of the downstream side oil passage portion is in the axis direction of the upstream side oil passage portion. The connecting oil passage portion is configured to be narrower than the oil passage width in the along direction, and the connecting oil passage portion is configured in a downstream narrowing state in which the oil passage width in the direction along the axial core direction is narrower toward the downstream side oil passage portion. It is preferable to have it.

According to this configuration, the connecting oil passage acts as a throttle to the lubricating oil flowing from the upstream oil passage to the downstream oil passage, and the oil passage width of the downstream oil passage portion is the upstream oil passage portion. Since it is narrower than the width of the oil passage, even if there is a change in the amount of oil in the upstream side oil passage, the amount of oil in the downstream side oil passage is stabilized, and a stable amount of lubrication is provided between the planetary gear and the planetary support shaft. Can be supplied with oil.

In the present invention
The second sun gear whose shaft core is located on the shaft core of the sun gear, the second planetary gear that meshes with the second sun gear, the second internal tooth gear that meshes with the second planet gear, and the planetary gear. A transmission gear that is meshed and transmits the rotation of the planetary gear to the second planetary gear is provided, the carrier having a second planetary support shaft that supports the second planetary gear, and the second sun. It is configured to rotate around the axis of the second sun gear together with the second planetary gear that revolves around the gear with the axis of rotation as the center of rotation, and is formed on the second planetary support shaft, and the second planetary support shaft and the said. The second planetary refueling passage for refueling between the second planetary gears, the solar refueling passage and the second planet refueling passage are connected, and the carrier extends in the radial direction and along the carrier. It is preferable that a second supply oil passage, which is formed in a state and takes in lubricating oil from the solar oil supply passage by the rotation of the carrier and supplies the taken-in lubricating oil to the second planetary oil supply passage, is provided. ..

According to this configuration, the rotation of the carrier causes the second supply oil passage to supply the lubricating oil taken in from the solar oil passage with the lubricating oil to the second planetary oil supply passage, and the second planetary oil supply passage is supplied. Since lubricating oil is supplied between the second planetary shaft and the second planetary gear, the sun is a composite planetary gear device in which the rotation of the first planetary gear is transmitted to the second planetary gear by the transmission gear. The gear, the first planetary gear and the second planetary gear can be rotated at high speed.

In the present invention
In the second supply oil passage, a second upstream side oil passage portion that opens to the solar oil supply passage, a second downstream side oil passage portion that opens to the second planetary oil supply passage, and the second upstream side oil passage portion. And a second connecting oil passage portion connecting the second downstream side oil passage portion, and the second supply oil passage portion is along the axis direction of the sun gear of the second downstream side oil passage portion. The width of the oil passage in the direction is configured to be narrower than the width of the oil passage in the direction along the axis direction of the second upstream side oil passage portion, and the second connecting oil passage portion is in the direction along the axis direction. It is preferable that the width of the oil passage in the above is narrower toward the oil passage portion on the second downstream side in a narrowed state on the downstream side.

According to this configuration, the second connecting oil passage portion acts to throttle the lubricating oil flowing from the second upstream side oil passage portion to the second downstream side oil passage portion, and the oil passage of the second downstream side oil passage portion acts. Since the width is narrower than the oil passage width of the second upstream side oil passage portion, even if there is a change in the oil amount in the second upstream side oil passage portion, the oil amount in the second downstream side oil passage portion is stabilized, and the second A stable amount of lubricating oil can be supplied between the two planetary gears and the second planetary support shaft.

In the present invention
It is preferable that the transmission gear is supported by the second planetary support shaft.

According to this configuration, a composite planetary gear device can be obtained with a simple structure in which the second planetary support shaft is used as the support shaft of the transmission gear.

In the present invention
The planetary gears are provided at a plurality of locations around the sun gear, the second planetary gears are provided in the same number as the number of the planetary gears, and the planetary support shafts of the planetary gears at the plurality of locations are provided. It is preferable that the planetary refueling passage is formed in the second planetary refueling passage, and the second planetary refueling passage is formed in the second planetary support shaft of the second planetary gear having the same number as the number of the planetary gears.

According to this configuration, lubricating oil is supplied by a planetary refueling passage between a planetary support shaft supporting each planetary gear of a plurality of planetary gears and the planetary gears to support each of the second planetary gears of the plurality of second planetary gears. Since the lubricating oil is supplied by the second planetary refueling passage between the second planetary shaft and the second planetary gear, the plurality of planetary gears and the plurality of second planetary gears can be rotated at high speed at low cost.

It is a left side view which shows the whole of a tractor. It is a diagram which shows the traveling transmission device. It is sectional drawing which shows the planetary gear device. It is a front view which shows the 1st sun gear, 1st planetary gear, 1st internal tooth gear and transmission gear. It is a rear view which shows the 2nd sun gear, the 2nd planetary gear, and the 2nd internal tooth gear. It is a perspective view which shows the 1st planetary gear, the 2nd planetary gear, a transmission gear and a carrier in a disassembled state. It is a perspective view which shows the carrier in a completed state. It is a front view which shows the 1st carrier part in the state which the 1st planetary gear, the transmission gear and the 2nd planetary gear are attached. It is sectional drawing which shows the refueling structure. It is a vertical sectional view of the 2nd carrier part. It is a perspective view which shows a part of the 2nd carrier part. It is explanatory drawing which shows the relationship between the speed change state of a continuously variable transmission, a speed range, and the rotation speed of the output shaft of a step division transmission part.

Hereinafter, embodiments that are an example of the present invention will be described with reference to the drawings.
In the following description, regarding the traveling vehicle body of the tractor, the direction of the arrow F shown in FIG. 1 is "front of the vehicle body", the direction of the arrow B is "rear of the vehicle body", the direction of the arrow U is "upper of the vehicle body", and the arrow D. The direction of is "lower of the car body", the direction of the front side of the paper is "left side of the car body", and the direction of the back side of the paper is "right side of the car body".

[Whole tractor]
The traveling vehicle body of the tractor is a vehicle body frame 5 and a vehicle body frame 5 composed of an engine 1, a clutch housing 2 provided at the rear of the engine 1, a mission case 3 connected to the clutch housing 2, a front frame 4, and the like. It has a pair of left and right front wheels 6 that are steerable and driveable at the front, and a pair of left and right rear wheels 7 that are driveable at the rear of the vehicle body frame 5. A driving portion 8 having an engine 1 is formed on the front portion of the traveling vehicle body. A driving unit 9 is formed at the rear of the traveling vehicle body. The driver unit 9 is provided with a driver's seat 10, a steering wheel 11 for steering and operating the front wheels 6, and a cabin 12 that covers the boarding space. At the rear of the vehicle body frame 5, a link mechanism 13 that connects various work devices such as a rotary tiller (not shown) so as to be able to move up and down, power from the engine 1 is taken out, and the taken out power is connected to the connected work device. A power take-out shaft 14 for transmission is provided.

[Traveling transmission device]
The power from the engine 1 is configured to be transmitted to the front wheels 6 and the rear wheels 7 by the traveling transmission device 15 shown in FIG.

As shown in FIG. 2, in the traveling transmission device 15, the power of the output shaft 1a of the engine 1 is transmitted to the input shaft 17 of the transmission case 3 via the main clutch 16. The power of the input shaft 17 is input to the main transmission unit 18 including the planetary gear device 18A, the output of the main transmission unit 18 is input to the step division transmission unit 19, and the output of the stage division transmission unit 19 is the forward / backward switching device 20. Is entered in. The output of the forward / backward switching device 20 is transmitted to the input shaft 22a of the rear wheel differential mechanism 22 via the rear wheel gear interlocking mechanism 21. A steering brake 23 and a deceleration mechanism 24 are provided in a power transmission system that transmits the output of the rear wheel differential mechanism 22 to the rear wheels 7. The reduction mechanism 24 is composed of a planetary gear mechanism. The power of the input shaft 22a of the rear wheel differential mechanism 22 is input to the front wheel transmission device 26 via the front wheel gear interlocking mechanism 25, and is transmitted from the front wheel transmission device 26 to the front wheel differential mechanism 28 via the rotary shaft 27. A parking brake 29 is provided on the front wheel gear interlocking mechanism 25.

Reference numeral 30 shown in FIG. 2 is a working transmission. In the work transmission 30, the power of the input shaft 17 is input via the rotary shaft 31 and the rear rotary shaft 32, and the input power is changed and transmitted to the power take-out shaft 14.

[Main transmission]
As shown in FIG. 2, the main transmission unit 18 includes a planetary gear device 18A and a continuously variable transmission device 18B. The planetary gear device 18A includes two planetary gear device units 50 and 60 arranged in the front-rear direction of the mission case 3. The front planetary gear device 50 and the input shaft 17 of the two planetary gear devices 50 and 60 are connected via the first gear interlocking mechanism 34. The continuously variable transmission 18B is composed of a hydrostatic type continuously variable transmission, and includes a variable displacement hydraulic pump P and a hydraulic motor M. The pump shaft and the input shaft 17 of the continuously variable transmission 18B are interlocked and connected via the second gear interlocking mechanism 35 and the rotating shaft 31. The motor shaft of the continuously variable transmission 18B and the front planetary gear unit 50 of the two planetary gear unit 50, 60 are connected via a third gear interlocking mechanism 36.

In the main transmission unit 18, the power from the engine 1 is changed by the stepless transmission 18B, and the changed power and the power transmitted from the engine 1 via the third gear interlocking mechanism 36 are the planetary gear device 18A. Is input to and is combined by the two planetary gear device units 50 and 60, and the combined power is output from the first output shaft 37a, the second output shaft 37b, and the third output shaft 37c configured on the triple shaft.

[Step-by-step transmission section]
As shown in FIG. 2, the step division transmission unit 19 has an output shaft 38 provided with four stage division clutches CL1 to CL4 and four stage division clutches CL1 to CL4 to which the output of the planetary gear device 18A is input. I have.

In the step division transmission unit 19, as shown in FIG. 3, the continuously variable transmission 18B and the four stage division clutches CL1 to CL4 are appropriately operated, so that the combined power from the planetary gear device 18A is divided into four stages. It is output from the output shaft 38 in stages according to the speed range of.

FIG. 12 is an explanatory diagram showing the relationship between the speed change state of the continuously variable transmission 18B, the speed range, and the rotation speed V of the output shaft 38 of the stepwise transmission unit 19. The vertical axis of FIG. 12 shows the rotation speed V of the output shaft 38. The horizontal axis of FIG. 12 indicates the shifting state of the continuously variable transmission 18B, “N” indicates a neutral state, and “-MAX” indicates the maximum speed shifting state in the reverse rotation direction. "+ MAX" indicates the maximum speed shift state in the forward rotation direction.

Of the four stage division clutches CL1 to CL4, when the first clutch CL1 is engaged and the continuously variable transmission 18B is operated for shifting, the power of the first output shaft 37a is powered by the first speed gear interlocking mechanism 39a and the first. The speed is changed by the clutch CL1 and the output is output from the output shaft 38. As shown in FIG. 12, as the rotation speed of the output shaft 38 becomes the rotation speed in the 1st speed range and the stepless speed changer 18B is changed from "-MAX" to "+ MAX", the output shaft 38 The rotation speed V of is steplessly increased from the zero speed [0] to the maximum speed [V1] in the 1st speed range.

Of the four stage division clutches CL1 to CL4, when the second clutch CL2 is engaged and the continuously variable transmission 18B is operated for shifting, the power of the third output shaft 37c is powered by the second speed gear interlocking mechanism 39b and the second. The speed is changed by the clutch CL2 and the output is output from the output shaft 38. As shown in FIG. 12, the rotation speed of the output shaft 38 becomes the rotation speed of the 2nd speed range higher than the 1st speed range, and the stepless speed changer 18B is changed from "+ MAX" to "-MAX". Along with this, the rotation speed V of the output shaft 38 increases steplessly from the lowest speed [V1] in the second speed range to the highest speed [V2] in the second speed range.

Of the four stage division clutches CL1 to CL4, when the third clutch CL3 is engaged and the continuously variable transmission 18B is operated for shifting, the power of the second output shaft 37b is powered by the third speed gear interlocking mechanism 39c and the third. The speed is changed by the clutch CL3 and the output is output from the output shaft 38. As shown in FIG. 12, the rotation speed of the output shaft 38 becomes the rotation speed of the 3rd speed range on the higher speed side than the 2nd speed range, and the stepless speed changer 18B is changed from [-MAX] to "+ MAX". As a result, the rotation speed V of the output shaft 38 increases steplessly from the lowest speed [V2] in the third speed range to the highest speed [V3] in the third speed range.

Of the four stage division clutches CL1 to CL4, when the fourth clutch CL4 is engaged and the continuously variable transmission 18B is operated for shifting, the power of the third output shaft 37c is powered by the fourth speed gear interlocking mechanism 39d and the fourth. The speed is changed by the clutch CL4 and the output is output from the output shaft 38. As shown in FIG. 12, the rotation speed of the output shaft 38 becomes the rotation speed of the 4th speed range on the higher speed side than the 3rd speed range, and the stepless speed changer 18B is changed from "+ MAX" to "-MAX". As a result, the rotation speed V of the output shaft 38 increases steplessly from the lowest speed [V3] in the 4-speed range to the highest speed [V4] in the 4-speed range.

[Forward / forward switching device]
As shown in FIG. 2, the forward / reverse switching device 20 includes an input shaft 40 interlocked with the output shaft 38 of the stepwise transmission unit 19, a forward clutch CLF and a reverse clutch CLR provided on the input shaft 40, and a forward clutch. The output shaft 42 is connected to the CLF via the forward gear mechanism 41f and is connected to the reverse clutch CLR via the reverse gear mechanism 41r.

In the forward / backward switching device 20, when the forward clutch CLF is turned on, the power transmitted from the step division transmission unit 19 to the input shaft 40 is converted into forward power by the forward clutch CLF and the forward gear mechanism 41f and output. It is output from the shaft 42. When the reverse clutch CLR is turned on, the power transmitted from the step division transmission unit 19 to the input shaft 40 is converted into reverse power by the reverse clutch CLR and the reverse gear mechanism 41r and output from the output shaft 42. The forward power and reverse power output from the output shaft 42 are transmitted to the rear wheel gear interlocking mechanism 21, and are transmitted to the input shaft 22a of the rear wheel differential mechanism 22 by the rear wheel gear interlocking mechanism 21.

[Front wheel transmission device]
As shown in FIG. 2, the front wheel transmission device 26 has a constant speed clutch provided on the input shaft 43 and the input shaft 43 connected to the input shaft 22a of the rear wheel differential mechanism 22 via the front wheel gear interlocking mechanism 25. It is provided with an output shaft 45 connected to the CLT, the speed-increasing clutch CLH, and the constant-speed clutch CLT via the constant-speed gear mechanism 44a, and connected to the speed-increasing clutch CLH via the speed-increasing gear mechanism 44b.

In the front wheel transmission device 26, when the constant velocity clutch CLT is engaged, the power transmitted from the input shaft 22a of the rear wheel differential mechanism 22 to the input shaft 43 causes the constant velocity clutch CLT and the constant velocity gear mechanism 44a. It is transmitted to the output shaft 45 via the output shaft 45 and is transmitted from the output shaft 45 to the front wheel differential mechanism 28. In this case, a state in which the pair of left and right front wheels 6 and the pair of left and right rear wheels 7 are driven with the average peripheral speed of the pair of left and right front wheels 6 and the average peripheral speed of the pair of left and right rear wheels 7 being substantially equal, so-called front and rear. A four-wheel drive state with constant wheel speed appears. When the speed-increasing clutch CLH is engaged, the power transmitted from the input shaft 22a of the rear wheel differential mechanism 22 to the input shaft 43 is transmitted to the output shaft 45 via the speed-increasing clutch CLH and the speed-increasing gear mechanism 44b. It is transmitted from the output shaft 45 to the front wheel differential mechanism 28. In this case, a state in which the pair of left and right front wheels 6 and the pair of left and right rear wheels 7 are driven in a state where the average peripheral speed of the pair of left and right front wheels 6 is faster than the average peripheral speed of the pair of left and right rear wheels 7, so-called. The four-wheel drive state of front wheel speed increase appears.

[Planetary gear device]
As shown in FIGS. 2 and 3, the planetary gear device 18A includes two planetary gear device units 50 and 60 arranged in the front-rear direction of the mission case 3. The planetary gear device 18A is configured as a compound planetary gear device. In the following, the front planetary gear unit 50 of the two planetary gear unit 50, 60 will be referred to as the first planetary gear unit 50, and the rear planetary gear unit 50 of the two planetary gear unit 50, 60 will be referred to. The section 60 will be referred to as a second planetary gear device section 60.

[1st planetary gear device]
As shown in FIGS. 1 Internal tooth gear 53 and a 1st planetary gear 52 that rotatably supports the 1st planetary gear 52 and revolves around the 1st sun gear 51, together with a shaft core X of the 1st sun gear 51 (see FIG. 4). ) Is provided with a carrier 70 that rotates about the center of rotation.

As shown in FIG. 3, the first sun gear 51 is rotatably supported by a sun support shaft configured by the rotation shaft 31. Hereinafter, the rotation shaft 31 is referred to as a sun support shaft 31. As shown in FIG. 2, the first sun gear 51 is interlocked and connected to the third gear interlocking mechanism 36. Specifically, as shown in FIG. 3, the boss portion 51a provided in the first sun gear 51 is extended to the front side of the carrier 70, and the third gear interlocking mechanism 36 is attached to the extended portion of the boss portion 51a. The transmission gear 36a of the above is interlocked and connected. The interlocking connection between the boss portion 51a and the transmission gear 36a is performed by spline engagement.

As shown in FIG. 4, the first planetary gears 52 are provided at three locations around the first sun gear 51. As shown in FIG. 3, each first planetary gear 52 is rotatably supported by the first planetary support shaft 54. A bush 55 is provided between the first planetary gear 52 and the first planetary support shaft 54.

As shown in FIG. 3, the first internal tooth gear 53 is rotatably supported by the boss portion 51a of the first sun gear 51. Specifically, the boss portion 53a provided in the first internal tooth gear 53 is fitted onto the boss portion 51a via a tubular member 56 located between the boss portion 53a and the boss portion 51a of the first sun gear 51. Has been done. As shown in FIG. 2, the first internal tooth gear 53 is interlocked with the first gear interlocking mechanism 34. Specifically, as shown in FIG. 3, the boss portion 53a of the first internal tooth gear 53 and the cylinder member 56 are interlocked and connected by spline engagement, and the cylinder member 56 and the transmission of the first gear interlocking mechanism 34 are transmitted. The gear 34a is interlocked and connected by spline engagement.

[2nd planetary gear device]
As shown in FIGS. The transmission gear 64 (see FIG. 4), which is meshed with the two internal tooth gears 63 and the first planetary gear 52 and transmits the rotation of the first planetary gear 52 to the second planetary gear 62, and the second planetary gear 62 can be rotated. A carrier 70 that rotates about the axis Z (see FIG. 5) of the second sun gear 61 together with the second sun gear 61 that revolves around the second sun gear 61. There are.

As shown in FIG. 3, the second sun gear 61 is supported by a portion of the third output shaft 37c that has entered the inside of the carrier 70. The axis Z of the second sun gear 61 is located on the axis Z of the first sun gear 51. The shaft core Z of the second sun gear 61 and the shaft core X of the first sun gear 51 are the same shaft core. As shown in FIG. 2, the second sun gear 61 is interlocked and connected to the third output shaft 37c. As shown in FIG. 3, the second sun gear 61 and the third output shaft 37c are interlocked and connected by spline engagement.

The second planetary gears 62 are provided at three locations around the second sun gear 61, as shown in FIG. The number of the second planetary gears 62 is the same as the number of the first planetary gears 52. As shown in FIG. 3, each second planetary gear 62 is rotatably supported by the second planetary support shaft 65.

As shown in FIG. 4, the transmission gear 64 is provided so as to correspond to the first planetary gear 52 at three locations and the second planetary gear 62 at three locations. The number of transmission gears 64 is the same as the number of the first planetary gears 52 and the number of the second planetary gears 62. As shown in FIG. 3, the transmission gear 64 is supported by a portion of the second planetary support shaft 65 located on the front side of the second planetary gear 62. The transmission gear 64 is interlocked with the second planetary gear 62, and transmits the rotation of the first planetary gear 52 input by meshing with the first planetary gear 52 to the second planetary gear 62. A bush 66 is provided between the second planetary gear 62 and the second planetary support shaft 65, and between the transmission gear 64 and the second planetary support shaft 65. In the present embodiment, the transmission gear 64 and the second planetary gear 62 are interlocked and connected by integrally forming the transmission gear 64 and the second planetary gear 62. The transmission gear 64 and the second planetary gear 62 may be interlocked and connected by the second planetary support shaft 65.

As shown in FIGS. 2 and 3, the second internal tooth gear 63 is supported by the front portion of the first output shaft 37a and is interlocked with the first output shaft 37a. Specifically, the interlocking connection between the second internal tooth gear 63 and the first output shaft 37a is performed by spline engagement between the boss portion 63a provided in the second internal tooth gear 63 and the first output shaft 37a. It has been.

[Carrier composition]
The carrier 70 of the first planetary gear device unit 50 and the carrier 70 of the second planetary gear device unit 60 are configured by the same carrier 70. The carrier 70 is configured as follows.

As shown in FIG. 3, the carrier 70 is supported by the boss portion 53a of the first internal tooth gear 53 and the boss portion 63a of the second internal tooth gear 63. A ball bearing 71 is provided between the carrier 70 and the boss portion 53a, and a ball bearing 72 is provided between the carrier 70 and the boss portion 63a. The carrier 70 is rotatably supported by the boss portion 53a and the boss portion 63a, and rotates around the axis X of the first sun gear 51 together with the first planetary gear 52 that revolves around the first sun gear 51. (See FIG. 4), and together with the second planetary gear 62 revolving around the second sun gear 61, it rotates around the axis Z of the second sun gear 61 (see FIG. 5).

As shown in FIG. 3, the carrier 70 includes a first planetary support shaft 54, a second planetary support shaft 65, a first sun gear 51, a second sun gear 61, a first planet gear 52, and a second planet gear. It includes a first carrier portion 70A that houses the 62 and the transmission gear 64, and a second carrier portion 70B that constitutes a lid for the first carrier portion 70A.

As shown in FIG. 6, the first carrier portion 70A and the second carrier portion 70B are configured to be separable in the axis direction of the first sun gear 51 and the axis direction of the second sun gear 61.

As shown in FIG. 6, the sun support shaft 31 is inserted into the central portion of the first carrier portion 70A, the front portion of the second output shaft 37b is inserted, and the front portion of the third output shaft 37c is further inserted. A first through hole 73 is provided. The first through hole 73 is configured as a spline hole that engages with the spline shaft portion 37s (see FIG. 3) of the second output shaft 37b. A sun gear accommodating space 74 accommodating the first sun gear 51 and the second sun gear 61 is provided at a position on the second carrier portion side (front side) of the first through hole 73 in a state of communicating with the first through hole 73. Has been done. The sun gear accommodating space 74 is opened toward the second carrier portion side, and the first sun gear 51 and the second solar gear 61 are incorporated from the second carrier portion side (front side) with respect to the sun gear accommodating space 74. It is configured to be possible.

Three first gear accommodation spaces 75, which separately accommodate three first planetary gears 52, and three second planetary gears 62, which separately accommodate three second planetary gears 62, around the sun gear accommodation space 74. A gear accommodation space 76 is provided. The three first gear accommodation spaces 75 and the three second gear accommodation spaces 76 are arranged in the carrier circumferential direction with one second gear accommodation space 76 located between the first gear accommodation spaces 75.

The second gear accommodating space 76 is configured to accommodate the transmission gear 64. The depth depth of the first sun gear 51 of the second gear accommodation space 76 in the direction along the axis direction is deeper than the depth depth of the first gear accommodation space 75 in the direction along the axis direction of the first sun gear 51. Has been done. As shown in FIG. 8, the first gear accommodating space 75 and the second gear accommodating space 76 communicate with each other in the carrier circumferential direction so that the first planetary gear 52 and the transmission gear 64 can mesh with each other. ..

As shown in FIGS. 7 and 8, in the first gear accommodating space 75, a portion of the first planetary gear 52 that meshes with the first internal tooth gear 53 projects from the first gear accommodating space 75 toward the outer periphery of the carrier. It is configured as follows. The second gear accommodating space 76 is configured such that a portion of the second sun gear 61 that meshes with the second internal tooth gear 63 projects from the second gear accommodating space 76 toward the outer peripheral side of the carrier.

As shown in FIG. 6, the first gear accommodating space 75 is opened toward the second carrier portion 70B at the second carrier portion side end portion (front end portion) of the first gear accommodating space 75, and the first gear accommodating space 75 is opened. A first opening 77 is provided to allow the first planetary gear 52 to be incorporated into the gear accommodation space 75. In the portion of the first carrier portion 70A on the side opposite to the side where the first opening 77 is located with respect to the first gear accommodating space 75, the first of the first planetary support shafts 54 is the first than the first planetary gear 52. A first support hole 78 for supporting the first end 54a (see FIGS. 3 and 6) of the first support shaft located on one end side of the planetary support shaft is provided. The first support shaft first support hole 78 is provided so as to communicate with the first gear accommodating space 75.

As shown in FIG. 6, the second gear accommodating space 76 is opened toward the second carrier portion 70B at the second carrier portion side end portion (front end portion) of the second gear accommodating space 76, and the second gear accommodating space 76 is opened to the second carrier portion 70B. A second opening 79 is provided to allow the second planetary gear 62 and the transmission gear 64 to be incorporated into the gear accommodation space 76. In the portion of the first carrier portion 70A on the side opposite to the side where the second opening 79 is located with respect to the second gear accommodating space 76, in the second planetary support shaft 65, the second planetary support rather than the transmission gear 64 The second support shaft 1st that supports the first end portion 65a (see FIGS. 3 and 6) of the second support shaft located on one end side of the shaft and located on one end side of the second planet support shaft with respect to the second planet gear 62. A support hole 80 is provided. The second support shaft first support hole 80 is provided so as to communicate with the second gear accommodating space 76.

As shown in FIG. 6, in the first carrier portion 70A, reinforcement is provided between the portion outside the carrier radial direction in the first gear accommodation space 75 and the portion outside the carrier radial direction in the second gear accommodation space 76. A section 81 is provided. Reinforcing portions 81 are provided at six locations. Each reinforcing portion 81 is integrally molded with the first carrier portion 70A. As shown in FIG. 8, the reinforcing portion 81 is located between the outer peripheral side portion of the first planetary gear 52 and the outer peripheral side portion of the transmission gear 64.

As shown in FIG. 3, in the rear portion of the first carrier portion 70A, the front portion of the first output shaft 37a and the boss portion of the second internal tooth gear 63 are located on the rear side of the sun gear accommodating space 74. A recessed portion 82 into which the 63a and the ball bearing 72 are inserted is provided.

The first carrier portion 70A is manufactured by casting, and the outer peripheral portion 84 (see FIG. 6) of the first carrier portion 70A is turned after casting. The mass of the first carrier portion 70A around the shaft core X of the first sun gear 51 and the shaft core Z of the second sun gear 61 becomes uniform, and the rotational vibration of the carrier 70 can be prevented.

The second carrier portion 70B includes an outer wall portion 85 and an inner wall portion 86, as shown in FIGS. 6, 10 and 11. The outer wall portion 85 and the inner wall portion 86 are connected by the outer peripheral portion of the second carrier portion 70B. As shown in FIGS. 3, 6 and 10, a second through hole 87 through which the boss portion 51a of the first sun gear 51 is inserted is provided in the central portion of the inner wall portion 86. In the center of the outer wall 85,
A third through hole 88 is provided through which the boss portion 51a of the first sun gear 51 is inserted, and the rear portion of the tubular member 56, the boss portion 53a of the first internal tooth gear 53, and the ball bearing 71 are inserted. Around the second through hole 87 in the second carrier portion 70B, the first lid portion 89 that closes the first opening 77 of the first gear accommodation space 75 and the second opening 79 of the second gear accommodation space 76 are closed. 2 The lid 90 is provided.

As shown in FIGS. 10 and 11, the first support shaft No. 2 located on the first lid portion 89 on the other end side of the first planetary support shaft of the first planetary support shaft 54 with respect to the first planetary gear 52. A first support shaft second support hole 91 for supporting the end portion 54b (see FIGS. 3 and 6) is provided. The first support shaft second support hole 91 is opened toward the first gear accommodation space 75, and the second carrier portion 70B is connected to the first carrier portion 70A to communicate with the first gear accommodation space 75. do. Of the second planetary support shaft 65, the second lid 90 is located on the other end side of the second planetary support shaft with respect to the second planetary gear 62, and is located on the other end side of the second planetary support shaft with respect to the transmission gear 64. A second support shaft second support hole 92 is provided to support the second end 65b (see FIGS. 3 and 6) of the second support shaft located at. The second support shaft second support hole 92 is opened toward the second gear accommodating space 76, and the second carrier portion 70B is connected to the first carrier portion 70A to communicate with the second gear accommodating space 76. do.

As shown in FIGS. 6 and 11, a connecting portion 93 for connecting the second carrier portion 70B to the first carrier portion 70A is provided at a portion around the third through hole 88 in the second carrier portion 70B. There is. The connecting portions 93 are provided corresponding to the six reinforcing portions 81 and are located at six locations. As shown in FIG. 7, each connecting portion 93 has a screw member in a bolt hole 94 (see FIG. 6) provided in the connecting portion 93 and a screw hole 95 (see FIG. 6) provided in the reinforcing portion 81. The connecting bolt 96 (see FIG. 6) is mounted and fastened to the reinforcing portion 81 by the connecting bolt 96. The connecting bolt 96 has a shaft core in a direction along the shaft core direction of the first sun gear 51. The reinforcing portion 81 is tightened and connected to the first carrier portion 70A in the direction along the axis direction of the first sun gear 51, and the second carrier portion 70B is connected to the first carrier portion 70A.

The carrier 70 can be obtained based on the following assembly method.
As shown in FIG. 6, the first planetary gear 52 is inserted into the first gear accommodating space 75 from the first opening 77 with the first planetary gear 52 attached to the first planetary support shaft 54, and the first support shaft 1st of the first planetary support shaft 54 is inserted. The end portion 54a is inserted into the first support hole 78 of the first support shaft. Then, the first end portion 54a of the first support shaft is supported by the first support hole 78 of the first support shaft. The first end portion 54a of the first support shaft is supported by the first carrier portion 70A.

As shown in FIG. 6, with the second planetary gear 62 and the transmission gear 64 attached to the second planetary support shaft 65, the second planetary support shaft 65 is inserted into the second gear accommodation space 76 through the second opening 79. The first end portion 65a of the support shaft is inserted into the first support hole 80 of the second support shaft. Then, the first end portion 65a of the second support shaft is supported by the first support hole 80 of the second support shaft. That is, the first end portion 65a of the second support shaft is supported by the first carrier portion 70A.

In this way, the three first planetary gears 52 are inserted into the first gear accommodation space 75, and the first end portion 54a of the first support shaft of the three first planet support shafts 54 is inserted into the first support hole 78 of the first support shaft. The three second planetary gears 62 and the three transmission gears 64 are inserted into the second gear accommodation space 76, and the first end portion 65a of the second support shaft of the three second planet support shafts 65 is the second support shaft. It is supported by the first support hole 80.

Next, the second support hole 91 of the first support shaft faces the second end portion 54b of the first support shaft of the first planet support shaft 54, and the second support hole 92 of the second support shaft is the second planet support shaft. The second carrier portion 70B is aligned with the first planetary support shaft 54 and the second planetary support shaft 65 so as to face the second end portion 65b of the second support shaft of 65, and the bolt hole 94 is formed in the connecting portion 93. And the connecting bolt 96 attached to the screw hole 95 is tightened. As the connecting portion 93 is tightened to the reinforcing portion 81 (first carrier portion 70A), the first support shaft second end portion 54b of each first planet support shaft 54 becomes the first support shaft second support hole 91. The second end portion 65b of the second support shaft of each second planet support shaft 65 enters into the second support hole 92 of the second support shaft.

When the tightening of the connecting bolt 96 is completed, the connecting portion 93 is tightened and connected to the reinforcing portion 81, the first planetary gear 52 is accommodated in the first gear accommodating space 75, and the second planetary gear 62 and the transmission gear 64 are first. The first opening 77 and the second opening 79 are accommodated in the two gear accommodation space 76 and are closed by the second carrier portion 70B, and the first carrier portion 70A and the second carrier portion 70B are interlocked with each other to form the first sun gear 51. The carrier 70 is in a state of rotating with the axis X of the second sun gear 61 as the center of rotation and the axis Z of the second sun gear 61 as the center of rotation. Further, the carrier 70 is in a state where the first carrier portion 70A and the second carrier portion 70B are connected by the reinforcing portion 81 and reinforced by the reinforcing portion 81.

[Structure of lubricating oil supply]
As shown in FIGS. Is provided. The solar refueling passages 100 are provided at two locations in the circumferential direction of the solar support shaft 31. The solar refueling passage 100 is provided so as to extend linearly along the axis of the sun support shaft 31 between the third output shaft 37c and the sun support shaft 31, and the third output shaft 37c and the sun support shaft 31 are provided. It is also possible to refuel between and. As shown in FIG. 3, the solar refueling passage 100 is refueled from the refueling passage 101 bored in the tubular portion 17a fitted to the front end portion of the solar support shaft 31. The tubular portion 17a is provided at the rear portion of the input shaft 17.

As shown in FIGS. 3 and 9, the first planetary support shaft 54 is provided with a first planetary oil supply passage 102 for supplying lubricating oil between the first planetary support shaft 54 and the first planetary gear 52. .. The first planetary refueling passage 102 is provided on three first planetary support shafts 54. Specifically, as shown in FIG. 9, the first planetary oil supply passage 102 is an upstream oil passage portion 102a bored in the first planetary support shaft 54 in a state along the axis direction of the first planetary support shaft 54. And, it is bored in the first planetary support shaft 54 in a state orthogonal to the axis of the first planetary support shaft 54, and the upstream oil passage portion 102a is connected to two places around the outer circumference of the first planetary support shaft 54. The downstream oil passage portion 102b and the like are provided.

In the first planetary oil supply passage 102, lubricating oil is supplied to the upstream oil passage portion 102a and flows from the upstream oil passage portion 102a into the downstream oil passage portion 102b, and from the downstream oil passage portion 102b to the first planetary support shaft 54 and the first planetary oil passage portion 102b. It is supplied between the first planetary shaft 54 and the first planetary gear 52 by being supplied to the bush 55 located between the one planetary gear 52.

As shown in FIGS. 3 and 9, the first planetary oil supply passage 102 is connected to the solar oil supply passage 100 by the first supply oil passage 103 provided inside the carrier 70. The first supply oil passage 103 extends along the radial direction of the carrier 70 and is provided along the carrier 70 (second carrier portion 70B), and the lubricating oil is taken in and taken in from the solar oil supply passage 100 by the rotation of the carrier 70. Lubricating oil is supplied to the first planetary oil supply passage 102. That is, the lubricating oil located in the first supply oil passage 103 is given centrifugal force by the rotation of the carrier 70 and flows toward the first planetary oil supply passage 102, and this flow causes the lubricating oil in the solar oil supply passage 100 to flow to the first. 1 It is taken into the supply oil passage 103 and is supplied from the first supply oil passage 103 to the first planetary oil supply passage 102.

The first supply oil passage 103 has a first upstream side oil passage portion 103a open to the solar oil supply passage 100, a first downstream side oil passage portion 103b open to the first planetary oil supply passage 102, and a first upstream side. A first connecting oil passage portion 103c for connecting the oil passage portion 103a and the first downstream side oil passage portion 103b is provided. The first upstream side oil passage portion 103a is formed by the front end portion of the first sun gear 51 and the rear end portion of the tubular member 56, and is formed through a through hole 51b provided in the boss portion 51a of the first sun gear 51. It is open to the solar refueling channel 100. The first downstream side oil passage portion 103b is formed by a first support shaft second support hole 91, an inner wall portion 86, and a ball bearing 71 of the second carrier portion 70B. The width of the first downstream side oil passage portion 103b in the direction along the axis direction of the first sun gear 51 is narrower than the width of the first upstream side oil passage portion 103a in the direction along the axis direction of the first sun gear 51. Has been done. The first connecting oil passage portion 103c is formed by an inclined portion 104 provided in a portion of the inner wall portion 86 near the second through hole 87, and a boss portion 53a of the first internal tooth gear 53. The width of the first connecting oil passage portion 103c in the direction along the axis direction of the first sun gear 51 is narrower toward the first downstream side oil passage portion side due to the action of the inclined portion 104. The first connecting oil passage 103c squeezes the lubricating oil flowing from the first upstream oil passage 103a toward the first downstream oil passage 103b, and the first downstream oil passage 103b is the first upstream. It is narrower than the side oil passage portion 103a, and even if the oil amount in the first upstream side oil passage portion 103a changes, the oil amount in the first downstream side oil passage portion 103b is stabilized.

As shown in FIGS. 3 and 9, the second planetary support shaft 65 is lubricated between the second planetary support shaft 65 and the transmission gear 64, and between the second planetary support shaft 65 and the second planetary gear 62. A second planetary refueling channel 105 for supplying oil is provided. The second planetary refueling passage 105 is provided on three second planetary support shafts 65. Specifically, as shown in FIG. 9, the second planetary oil supply passage 105 is an upstream oil passage portion 105a bored in the second planetary support shaft 65 in a state along the axis direction of the second planetary support shaft 65. , It is bored in the second planetary support shaft 65 in a state orthogonal to the axis of the second planetary support shaft 65, and the upstream oil passage portion 105a is used as the transmission gear 64 in the outer circumference of the second planetary support shaft 65. Two downstream oil passage portions 105b are separately connected to the corresponding portion and the portion corresponding to the second planetary gear 62 in the outer circumference of the second planetary shaft 65. The downstream oil passage portion 105b is open at two locations around the outer circumference of the second planetary support shaft 65.

In the second planetary refueling channel 105, lubricating oil is supplied to the upstream oil passage portion 105a and flows from the upstream oil passage portion 105a into the two downstream oil passage portions 105b, and from one downstream oil passage portion 105b to the second planetary branch. It is supplied between the second planetary support shaft 65 and the transmission gear 64 by being supplied to the bush 66 located between the shaft 65 and the transmission gear 64, and is supplied from the other downstream oil passage portion 105b to the second planetary support shaft 65. It is supplied between the second planetary shaft 65 and the second planetary gear 62 by being supplied to the bush 55 located between the second planetary gears 62.

As shown in FIGS. 3 and 9, the second planetary oil supply passage 105 is connected to the solar oil supply passage 100 by the second supply oil passage 106 provided inside the carrier 70. The second supply oil passage 106 extends along the radial direction of the carrier 70 and is provided along the carrier 70 (second carrier portion 70B), and the lubricating oil is taken in and taken in from the solar oil supply passage 100 by the rotation of the carrier 70. Lubricating oil is supplied to the second planetary refueling passage 105. That is, the lubricating oil located in the second supply oil passage 106 is subjected to centrifugal force by the rotation of the carrier 70 and flows toward the second planetary oil supply passage 105, and this flow causes the lubricating oil in the solar oil supply passage 100 to flow to the second. 2 It is taken into the supply oil passage 106 and is supplied from the second supply oil passage 106 to the second planetary oil supply passage 105.

The second supply oil passage 106 is a second upstream side oil passage portion 106a open to the solar oil supply passage 100, a second downstream side oil passage portion 106b open to the second planetary oil supply passage 105, and a second upstream side. A second connecting oil passage portion 106c connecting the oil passage portion 106a and the second downstream side oil passage portion 106b is provided. The second upstream side oil passage portion 106a is formed by the front end portion of the first sun gear 51 and the rear end portion of the tubular member 56, and is formed through a through hole 51b provided in the boss portion 51a of the first sun gear 51. It is open to the solar refueling channel 100. The second downstream side oil passage portion 106b is formed by a second support shaft second support hole 92, an inner wall portion 86, and a ball bearing 71 of the second carrier portion 70B. The width of the second downstream side oil passage portion 106b in the direction along the axis direction of the first sun gear 51 is narrower than the width of the second upstream side oil passage portion 106a in the direction along the axis direction of the first sun gear 51. Has been done. The second connecting oil passage portion 106c is formed by an inclined portion 104 provided in a portion of the inner wall portion 86 near the second through hole 87, and a boss portion 53a of the first internal tooth gear 53. The width of the second connecting oil passage portion 106c in the direction along the axis direction of the first sun gear 51 is narrower toward the second downstream side oil passage portion side due to the action of the inclined portion 104. The second connecting oil passage portion 106c squeezes the lubricating oil flowing from the second upstream side oil passage portion 106a to the second downstream side oil passage portion 106b, and the second downstream side oil passage portion 106b acts as a second upstream. It is narrower than the side oil passage portion 106a, and even if the oil amount in the second upstream side oil passage portion 106a changes, the oil amount in the second downstream side oil passage portion 106b is stabilized.

In the present embodiment, the first supply oil passage 103 for refueling the three first planetary refueling passages 102 and the second supply oil passage 106 for refueling the three second planetary refueling passages 105 are located in the circumferential direction of the carrier 70. It is provided in a state of communication.

Lubricating oil supplied from the refueling passage 101 to the solar refueling passage 100 is supplied from the solar refueling passage 100 between the solar support shaft 31 and the first solar gear 51. Further, it is supplied from the solar refueling passage 100 between the solar support shaft 31 and the third output shaft 37c. By rotating the carrier 70, the lubricating oil located in the solar refueling passage 100 is taken into the first supply oil passage 103 and supplied from the first supply oil passage 103 to the first planetary refueling passage 102, and is supplied to the first planetary refueling passage. It is supplied from 102 between the first planetary shaft 54 and the first planetary gear 52. Further, as the carrier 70 rotates, the lubricating oil located in the solar oil supply passage 100 is taken into the second supply oil passage 106 and supplied from the second supply oil passage 106 to the second planetary oil supply passage 105, and the second planet is supplied. It is supplied from the oil supply passage 105 between the second planetary support shaft 65 and the transmission gear 64, and between the second planetary support shaft 65 and the second planetary gear 62.

[Another Embodiment]
(1) In the above-described embodiment, the three planetary gears 52 and the three second planetary gears 62 are provided, but even those provided with two or four or more planetary gears and the second planetary gears. good.

(2) In the above-described embodiment, the second sun gear 61, the second planetary gear 62, the second internal tooth gear 63 and the transmission gear 64 are provided, but the sun gear (first sun gear) 51 and the planetary gear (2) Only the first planetary gear) 52 and the internal tooth gear (first internal tooth gear) 53 may be provided.

(3) In the above-described embodiment, the downstream oil passage portion is narrower than the upstream oil passage portion.
The width of the connecting oil passage is narrower toward the downstream side oil passage, and the width of the second downstream side oil passage is narrower than that of the second upstream side oil passage, so that the second connecting oil passage is narrower. The width of the oil passage is narrower toward the second downstream oil passage, but the width of the downstream oil passage and the width of the upstream oil passage are the same, and the width of the second downstream oil passage is the same. The width may be the same as the width of the second upstream side oil passage portion.

The present invention can be applied to a planetary gear device provided in various vehicles such as a combine harvester and a multipurpose vehicle in addition to a tractor.

51 Sun gear (1st sun gear)
52 Planetary gears (1st planetary gears)
53 Internal tooth gear (first internal tooth gear)
54 Planetary Axis (1st Planetary Axis)
61 2nd sun gear 62 2nd planetary gear 63 2nd internal tooth gear 64 transmission gear 65 2nd planetary support shaft 70 carrier 100 solar refueling path 102 planetary refueling path (1st planetary refueling path)
103 Supply oil passage (first supply oil passage)
103a Upstream oil passage (first upstream oil passage)
103b Downstream oil passage (1st downstream oil passage 9)
103c connecting oil passage (first connecting oil passage)
105 2nd planetary oil supply passage 106 2nd supply oil passage 106a 2nd upstream side oil passage 106b 2nd downstream oil passage 106c 2nd connection oil passage X axis Z axis core

Claims (6)

The sun gear, the planetary gear that meshes with the sun gear, the internal tooth gear that meshes with the planetary gear, and the planetary gear that rotatably supports the planetary gear and revolves around the sun gear. A planetary gear device equipped with a carrier that rotates around the axis of the sun gear as the center of rotation.
A solar refueling path formed on the outer peripheral portion of a sun support shaft that rotatably supports the sun gear and supplying lubricating oil between the sun gear and the sun support shaft.
A planetary refueling path formed on a planetary support shaft provided on the carrier in a state of rotatably supporting the planetary gear and supplying lubricating oil between the planetary support shaft and the planetary gear.
The solar refueling passage and the planetary refueling passage are connected to each other, and the carrier is formed in a state of extending along the radial direction and along the carrier, and the lubricating oil is taken in from the solar refueling passage by the rotation of the carrier. , A planetary gear device provided with a supply oil passage for supplying the taken-in lubricating oil to the planetary oil supply passage. The upstream oil passage portion that opens to the solar oil supply passage, the downstream oil passage portion that opens to the planetary oil supply passage, the upstream oil passage portion, and the downstream oil passage portion are connected to the supply oil passage. With a connecting oil passage,
In the supply oil passage, the oil passage width in the direction along the axis direction of the sun gear of the downstream side oil passage portion is narrower than the oil passage width in the direction along the axis direction of the upstream side oil passage portion. Consists of
The planetary gear device according to claim 1, wherein the connecting oil passage portion is configured such that the oil passage width in the direction along the axis direction is narrower toward the downstream side oil passage portion. The second sun gear whose shaft core is located on the shaft core of the sun gear, the second planetary gear that meshes with the second sun gear, the second internal tooth gear that meshes with the second planet gear, and the planetary gear. A transmission gear that is meshed and transmits the rotation of the planetary gear to the second planetary gear is provided.
The carrier has a second planetary support shaft that supports the second planetary gear, and has the second planetary gear that revolves around the second sun gear and the axis of the second sun gear as the center of rotation. Configured to rotate,
A second planetary refueling passage formed on the second planetary shaft and refueling between the second planetary shaft and the second planetary gear.
The solar refueling passage and the second planetary refueling passage are connected to each other, and the carrier is formed in a state of extending along the radial direction and along the carrier, and the lubricating oil is supplied from the solar refueling passage by the rotation of the carrier. The planetary gear device according to claim 1 or 2, further comprising a second supply oil passage for feeding the incorporated lubricating oil to the second planetary oil supply passage. In the second supply oil passage, a second upstream side oil passage portion that opens to the solar oil supply passage, a second downstream side oil passage portion that opens to the second planetary oil supply passage, and the second upstream side oil passage portion. And a second connecting oil passage portion connecting the second downstream side oil passage portion are provided.
In the second supply oil passage, the oil passage width in the direction along the axis direction of the sun gear of the second downstream side oil passage portion is the oil in the direction along the axis direction of the second upstream side oil passage portion. It is configured to be narrower than the road width,
The planetary gear device according to claim 3, wherein the second connecting oil passage portion is configured such that the oil passage width in the direction along the axis direction is narrower toward the second downstream side oil passage portion. .. The planetary gear device according to claim 3 or 4, wherein the transmission gear is supported by the second planetary support shaft. The planetary gears are provided at a plurality of locations around the sun gears.
The number of the second planetary gears is the same as the number of the planetary gears.
The planetary refueling passage is formed on the planetary support shaft of the planetary gears at the plurality of locations.
The planetary gear device according to any one of claims 3 to 5, wherein the second planetary refueling passage is formed on the second planetary shaft of the second planetary gear having the same number as the number of planetary gears.

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